Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
  • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
  • B01D—SEPARATION
  • B01D45/00—Separating dispersed particles from gases or vapours by gravity, inertia, or centrifugal forces
  • B01D45/12—Separating dispersed particles from gases or vapours by gravity, inertia, or centrifugal forces by centrifugal forces
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B13/00—Compression machines, plants or systems, with reversible cycle
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
  • F25B43/006—Accumulators
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
  • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
  • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
  • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
  • F25B2400/02—Centrifugal separation of gas, liquid or oil
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
  • F25B2400/07—Details of compressors or related parts
  • F25B2400/075—Details of compressors or related parts with parallel compressors
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B2500/00—Problems to be solved
  • F25B2500/01—Geometry problems, e.g. for reducing size
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B31/00—Compressor arrangements
  • F25B31/002—Lubrication
  • F25B31/004—Lubrication oil recirculating arrangements

Definitions

• Oil separator and outdoor unit having the same
• the present invention relates to an oil separator mainly used for a refrigeration system or an air conditioner, for separating oil taken out together with refrigerant gas from a compressor from the refrigerant gas and returning the oil to the compressor; and
• the present invention relates to an outdoor unit using the oil separator.
• FIG. 14 is a diagram showing the internal structure of a conventional oil separator described in Japanese Patent Application Laid-Open No. 8-319815.
• reference numeral 101 denotes a shell, which is a substantially cylindrical body.
• One of the open ends 101 a has a small diameter and the other open end 101 b has a large diameter. 1 Taper on a side
• the other opening end 101b is formed with a flange portion 101f extending in the radial direction. Also, on the opening 101 b side, an inlet pipe 102 is formed integrally with the shell 101, and the inlet port 1 is formed in the tangential direction of the inner cylindrical surface of the shell 101.
• 0 2a is open.
• Reference numeral 103 denotes an outflow pipe, which forms a cylindrical body having a flange portion 104 formed in an intermediate portion.
• the flange portion 104 has a flange portion 104f, which is a flange of the shell 101. It is joined to the part 101 f in close contact.
• the gas-liquid mixed fluid of gas and oil mist flows from the inflow pipe 102 in the tangential direction of the inner wall surface of the shell 101, and swirls in the shell 101, The oil mist adheres to and separates from the inner wall surface of the shell 101 due to centrifugal force, moves downward along the inner wall surface, and is discharged from the open end 101a.
• FIG. 15 is a partial vertical cross-sectional view of a conventional oil separator described in Japanese Patent Application Laid-Open No. 9-177759.
• reference numeral 201 denotes a shell, which is provided with a cylindrical portion 202a, and a flange portion 202b protruding outward at the upper end thereof.
• an inverted conical cylindrical body 202c is integrally attached to a lower end of the cylindrical part 202a, and an oil recovery part 202d is integrally attached to a lower opening thereof.
• an inflow pipe 203 is attached to an opening near the upper end of the cylindrical portion 202a.
• a circular lid 204 is fixed to the flange portion 202b of the cylindrical portion 202a. At the center of the lid 204, an outflow pipe 205 is provided so as to penetrate the lid 204.
• a non-woven fabric 206 having a predetermined shape is affixed inside the outflow pipe 205.
• the gas containing oil mist flows into the shell 201 from the inflow pipe 203, and the outflow pipe 200 projecting into the cylindrical part 202a and the cylindrical part 202a. Turn in the cylindrical space of 5. Due to the cyclone effect caused by this gas swirl, large oil mist in the gas, particularly with a particle size of about 5 zm or more, collides with the inner wall surface of the shell 201 and condenses. As a result, it falls along the inner wall surface and flows out to the oil recovery section 202d.
• the oil mist having a small particle diameter that has not collided with the inner wall surface of the shell 201 flows into the outlet pipe 205 together with the gas. Due to the influence of the swirling in the cylindrical space K, the gas spirally turns and proceeds upward without going straight through the outflow pipe 205.
• the velocity distribution of the gas flow at that time is such that the velocity near the pipe wall is large and the velocity at the center is very small. Then, the gas spirally circling the peripheral portion at a high speed hits the nonwoven fabric 206 adhered to the tube wall and is adsorbed.
• FIG. 16 is a configuration diagram showing a conventional gas-liquid separator described in Japanese Utility Model Application Laid-Open No. 6-6402, and FIG. 17 is a cross-sectional view as viewed from above.
• the gas-liquid separator 301 includes a shell 304 formed by combining a cylinder 302 and a cone 303.
• An inflow pipe 305 for introducing a two-phase flow from the tangential direction is provided on the cylinder 302 side of the shell 304, and the two-phase flow swirls in the shell 304 to generate centrifugal force.
• the liquid is separated into liquid and vapor, and the liquid adheres to the inner wall of the shell 304 by its own adhesive force.
• the inner wall of the shell 304 is provided with a wick for guiding the separated liquid to the cone 303.
• the shell 304 has a partition plate 3 for dividing the flow into the cylinder 302 side and the cone 303 side. 07 is provided.
• the partition plate 307 is provided with a small hole 308 for communicating the cylinder 302 side and the cone 303 side to make the pressure inside the shell 304 uniform, and A gap 309 is provided between the outer periphery of the partition plate 307 and the inside of the shell 304.
• a wire wick folded from a wire mesh as a coarse wick is accommodated to form a liquid reservoir 310 for accumulating liquid.
• a liquid outlet pipe 311 that guides the liquid out of the shell 304 is formed at the top of the cone 303.
• An outflow pipe 312 is formed at the center of the cylinder 302 side in the shell 304 divided by the partition plate 307 through the end plate 302a of the cylinder 302 side. ing.
• the layout relationship between the outflow pipe and the inflow pipe has not been properly optimized, so that the high pressure and low pressure of the refrigeration cycle caused by load fluctuations and the like have been reduced.
• the oil separator In systems where the flow rate of the refrigerant generated due to fluctuations changes, or in systems where the capacity of the compressor is controlled according to the load, even when the refrigerant flow rate is high, the oil separator It was not possible to properly cope with the problem that the swirling speed of the gas inside the vessel decreased and the oil separation efficiency decreased due to the cyclone effect.
• the oil separation efficiency is the ratio of the flow rate of oil discharged from the discharge pipe per unit time to the amount of oil flowed into the oil separator per unit time. In order to eliminate this adverse effect, if the diameter of the inflow pipe is reduced in accordance with the low flow rate, the pressure loss increases when the gas velocity flowing into the shell increases, and the efficiency of the refrigeration cycle decreases.
• the present invention has been made to solve the above-described problems, and the present invention has been made in such a manner that when the speed of gas flowing into an oil separator changes or the flow rate of oil flowing into the oil separator changes, the oil stays in a shell. It is an object of the present invention to provide an oil separator in which the pressure loss and the oil separation efficiency change are small even if the amount of oil to be changed varies easily, and the production cost is low.
• An oil separator includes: a shell having a cylindrical portion; a tapered portion formed integrally with a lower portion of the cylindrical portion; And a discharge pipe connected to an opening provided at the lower part of the tape 1 ', and a tangential direction of the inner wall surface of the cylindrical portion, and the shell
• An oil separator having an inflow pipe into which a gas-liquid two-phase flow flows, wherein a distance between the opening and an inner end of the shell of the outflow pipe is at least 5 times an inner diameter of the inflow pipe. It is characterized by the following.
• an oil separator includes a shell having a cylindrical portion, a downwardly squeezed theno, which is integrally formed at a lower portion of the cylindrical portion, and a shell having an upper portion extending from the upper portion of the shell.
• An outlet pipe inserted so that its central axis is coaxial with a discharge pipe connected to an opening provided at a lower portion of the taper portion, and a tangential direction of an inner wall surface of the cylindrical portion,
• An oil separator having an inflow pipe through which a gas-liquid two-phase flow flows into the inside of the shell, wherein an inner end of the shell of the outflow pipe extends downward from a center of an inner diameter of the inflow pipe. It is characterized by being located at least 5 times the inner diameter.
• an oil separator includes: a shell having a cylindrical portion, a tapered portion formed integrally with a lower portion of the cylindrical portion, and tapered downward; An outlet pipe inserted so that its axis becomes coaxial, a discharge pipe connected to an opening provided at a lower portion of the taper portion, and a tangential direction of an inner wall surface of the cylindrical portion, and the shell An inflow pipe for flowing a gas-liquid two-phase flow therein, wherein the inflow pipe has a straight pipe portion connected to the cylindrical portion, and the length of the straight pipe portion is: It is characterized by being at least eight times the inner diameter of the inflow pipe.
• an oil separator includes: a shell having a cylindrical portion, a tapered portion formed integrally with a lower portion of the cylindrical portion, and tapered downward; An outlet pipe inserted so that its axis is coaxial, a discharge pipe connected to an opening provided at a lower portion of the taper portion, and an inner wall surface of the cylindrical portion are connected.
• An oil separator having an inflow pipe connected in a linear direction and flowing a gas-liquid two-phase flow into the inside of the shell, wherein the inflow pipe has a first straight pipe portion connected to the cylindrical portion, A bent pipe having a second straight pipe section which is at an angle of 90 degrees to the shell direction with respect to the first straight pipe section.
• an oil separator includes: a shell having a cylindrical portion; a downwardly-squeezed teno portion formed integrally with a lower portion of the cylindrical portion; An outlet pipe inserted so that its central axis is coaxial with the outlet, a discharge pipe connected to an opening provided at a lower portion of the taper portion, and a tangential direction of an inner wall surface of the cylindrical portion, the shell being connected to the shell.
• An oil separator having an inflow pipe into which a gas-liquid two-phase flow flows, wherein the inflow pipe has a helical shape about a central axis of the shell.
• the shell has a tapered portion formed in an upper part of the cylindrical portion and integrally formed with the cylindrical portion and narrowed upward.
• the inflow pipes are connected to the cylindrical portion so as to be equally spaced at the same height in the vertical direction.
• the outdoor unit according to the present invention includes a compressor, any one of the above oil separators having an inflow pipe connected to the compressor, a capillary tube connected to a discharge pipe of the oil separator, A valve connected to the pipe in parallel with the capillary, an oil return circuit connected to the capillary and the valve, an accumulator connected to the oil return circuit and the compressor, and the oil separator.
• the outdoor unit includes a plurality of compressors, the oil separator in which each inlet pipe is connected to each of the plurality of compressors, and a capillary tube connected to a discharge pipe of the oil separator.
• a valve connected to the discharge tube so as to be in parallel with the capillary tube;
• An oil return circuit connected to the capillary tube and the valve;
• an accumulator connected to the oil return circuit and the plurality of compressors;
• a four-way valve connected to an outlet pipe of the oil separator; and the four-way valve.
• a heat exchanger connected to the heat exchanger.
• the valve is opened only when the compressor is started.
• FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle according to Embodiment 1 of the present invention.
• FIG. 2 is an upper cross-sectional view of the oil separator according to Embodiment 1 of the present invention.
• FIG. 3 is a side sectional view of the oil separator according to Embodiment 1 of the present invention.
• FIG. 4 is a diagram showing the relationship between the slag 2 and the oil separation efficiency.
• FIG. 5 is a diagram showing a state of a gas-liquid two-phase flow in the oil separator.
• FIG. 6 is a diagram showing a state of a gas-liquid two-phase flow in the oil separator.
• FIG. 7 is a diagram showing the relationship between L1 and oil separation efficiency.
• FIG. 8 is a diagram showing the relationship between L3 and oil separation efficiency.
• FIG. 9 is a top sectional view of the oil separator.
• FIG. 10 is a top sectional view of the oil separator.
• FIG. 11 is a refrigerant circuit diagram of a refrigeration cycle according to Embodiment 2 of the present invention.
• FIG. 12 is an upper cross-sectional view of an oil separator according to Embodiment 2 of the present invention.
• FIG. 13 is a side sectional view of an oil separator according to Embodiment 2 of the present invention.
• FIG. 14 is an internal structure diagram of a conventional oil separator.
• FIG. 15 is a partial longitudinal sectional view of a conventional oil separator.
• FIG. 16 is a structural diagram of a conventional gas-liquid separator.
• FIG. 17 is a top sectional view of a conventional gas-liquid separator. BEST MODE FOR CARRYING OUT THE INVENTION
• FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle equipped with an oil separator according to Embodiment 1 of the present invention.
• the refrigeration cycle is composed of one outdoor unit 1 and indoor unit 20 a s 20, and a liquid pipe 30 and a gas pipe 31 1 connecting the outdoor unit 1 and indoor units 20 a and 20 b. It is mainly composed of
• the outdoor unit 1 includes a compressor 2, an oil separator 3 connected to the compressor 2, a four-way valve 4 connected to the oil separator 3, and one port connected to the four-way valve 4 and the other port.
• the heat source side heat exchanger 5 whose port is connected to the liquid pipe 30, the accumulator 6 connected to the compressor 2, the solenoid valve 7 connected to the oil separator 3, and the solenoid valve 7 are arranged in parallel. It mainly comprises a capillary tube 8 connected to the oil separator 3 and an oil return circuit 9 connected to the solenoid valve 7 and the capillary tube 8 and the accumulator.
• the four-way valve 4 is also connected to the gas pipe 31.
• the indoor unit 20a includes a throttle device 21a connected to the liquid pipe 31 and a load side having one port connected to the throttle apparatus 21a and the other port connected to the gas pipe 30. It mainly consists of a heat exchanger 22a. Similarly, the indoor unit 20b is also mainly composed of the expansion device 21b and the load-side heat exchanger 22b. Next, the operation of the refrigeration cycle of FIG. 1 will be described.
• the liquid refrigerant may be stagnated in the compressor 2 .
• the compressor 2 When the compressor 2 is started, the refrigerant liquid including the refrigerating machine oil in the compressor 2 sharply drops due to the pressure drop in the compressor shell. The phenomenon of evaporation and foaming occurs, and a large amount of the mixture of the refrigerant and the refrigerating machine oil flows into the oil separator 3 from the compressor 2.
• the solenoid valve 7 is opened, and the liquid mixture of the refrigerant liquid and the oil is returned from the oil separator 3 to the inlet of the accumulator 7 through the oil return circuit 9.
• FIG. 2 is an upper cross-sectional view of the oil separator 3, and FIG.
• reference numeral 50 denotes a shell, which has a cylindrical shape with both ends narrowed in a taper shape, and has a cylindrical portion, a lower taper portion below the cylindrical portion, and an upper portion above the upper portion. It has a configuration with a taper part.
• Reference numeral 51 denotes a cylindrical outlet pipe, which penetrates the top of the upper taper of the shell 50, is inserted into the shell 50, and is the center of the ⁇ I outlet pipe 51 and the shell 50. The axes are fixed so that they are coaxial.
• Reference numeral 52 denotes a discharge pipe, which is fixed to a lower opening 50a formed at the top of the lower tapered portion of the shell 50.
• Reference numeral 53 denotes an inflow pipe, which has a cylindrical shape with a diameter of D and is connected in a tangential direction to an inner wall surface of a cylindrical portion (a portion not narrowed down to a taper shape) of the shell 50.
• the end 51 a of the part of the outflow pipe 51 inserted into the shell 50 is located at a distance of 1 below the center of the inner end of the shell of the inflow pipe 53, and the lower opening of the shell 50. It is located at a distance of L2 upward from 50a.
• the gas-liquid two-phase flow that has flowed into the shell 50 spirally turns down in the shell 50. Due to this swirling, a centrifugal oil mist (fine particles of refrigerating machine oil) collides with and adheres to the inner peripheral surface of the shell 50, and a cyclone effect occurs. It is gradually separated from the refrigerant gas.
• the refrigerant gas from which the oil mist is separated flows out of the outlet pipe 51, and the refrigerating machine oil attached to the inner wall surface of the shell 50 descends on the inner wall surface of the shell 50 by the action of gravity, and is discharged from the outlet pipe 52.
• the discharged gas flows through the oil return circuit 9 via the capillary 8 and returns to the compressor 2 via the accumulator 6.
• the oil separation efficiency of the refrigerating machine oil in such an oil separator depends on the position of the outflow pipe 51 in the shell 50, that is, the end 51a of the outflow pipe 51 and the shell of the inflow pipe 53.
• Fig. 4 is a graph showing the relationship between L2 and oil separation efficiency obtained as a result of the experiment. This experiment assumes that the oil flow rate in the oil separator is large, and the refrigerant flow rate is 6%. The test was performed in an environment of 50 to 680 kgZh, an oil circulation rate of 2.4 to 2.6%, and an inflow pipe diameter (inner diameter) D of 19.8 mm. The oil flow rate is obtained by multiplying the refrigerant flow rate by the oil circulation rate.
• the shell remains in a mortar-like shape while rotating on the inner wall 50.
• gas is entrained from the center and the gas-liquid two-phase flow As a result, it flows out of the discharge pipe 52. Therefore, the oil flowing into the oil return circuit 9 contains gas, and the pressure loss in the oil return circuit 9 increases, and it becomes impossible to secure a sufficient oil return amount.
• the thickness of the oil film attached to the inner wall surface of the shell 50 becomes further thicker, and at the lower part of the shell 50, the droplets are released again from the thickened oil film, so that the oil separation efficiency is reduced.
• the distance L 2 between the upper part 51 a of the outflow pipe 51 in the shell 50 and the lower opening 50 a of the shell 50 is 5 D or more, the liquid film below the shell 50 becomes a shell.
• the separated oil is discharged from the discharge pipe 52, gas is entrapped from the center even when the separated oil is discharged from the discharge pipe 52. Instead, the oil is discharged from the discharge pipe 52 as a single-phase oil. As a result, pressure loss in the oil return circuit 9 is suppressed, and the separated oil can be discharged smoothly.
• the oil separation efficiency depends on the number of turns of the airflow swirling in the shell 50, the number of turns can be reduced by connecting the inner end of the inlet pipe 53 with the end of the shell of the outlet pipe 51. What is necessary is just to secure the distance between them. From this, as shown in FIG. 7, the oil separation efficiency is improved by setting the position of the lower end of the outflow pipe 51 and the inner end of the shell of the inflow pipe 53 at 5 D or more. Therefore, by taking the positions of the inner ends of the shells of the outflow pipe 51 and the inflow pipe 53 at 5 D or more, even when the refrigerant flow rate is reduced, the air flow in the shell 50 necessary for oil separation even when the refrigerant flow rate is reduced And the oil separation efficiency is improved.
• FIG. 8 is a diagram showing the relationship between the length L 3 of the straight pipe portion from the inner end of the shell of the inflow pipe 53 and the oil separation efficiency, obtained as a result of the experiment.
• the first straight pipe portion 54a and the second straight pipe portion 54b may be formed by bending the first straight pipe portion 54a and the second straight pipe portion 54b.
• the inflow pipe 53 may be configured to have a spiral shape such that the center is the same as the center of the shell 50 on the outer periphery of the shell 50.
• the refrigerating machine oil flows unevenly to the outer periphery of the inflow pipe 53, so that the oil separation efficiency is improved.
• the upper part of the oil separator 3 has a tapered shape, so that the number of parts can be reduced as compared with the case where the upper part is formed by a flat lid, and The thickness required to obtain the required strength can be reduced, and the weight can be reduced.
• FIG. 11 is a refrigerant circuit diagram showing a refrigeration cycle according to Embodiment 2 of the present invention.
• the refrigerant cycle of FIG. 1 two compressors on the outdoor unit side are provided, and these two are connected to an oil separator. It was made. Note that, in FIG. 11, the same reference numerals are given to the same or equivalent components as in FIG. 1, and the description will be omitted.
• reference numerals 2a and 2b denote compressors, which are connected to the oil separator 3 via check valves 10a and 10b, respectively.
• the operation in the refrigeration cycle of FIG. 11 will be described.
• the liquid refrigerant may stagnate in the compressor 2a and the compressor 2b.
• the solenoid valve 7 is opened and the refrigerant liquid and the oil are supplied from the oil separator 3 to the inlet of the accumulator 6. Return the mixture of This prevents the oil separator 3 from overflowing and taking oil out of the system of the outdoor unit.
• the compressors 2a and 2b one by one with a time lag, the effect of preventing the oil separator 3 from overflowing is further enhanced.
• the compressor 2a and the compressor 2b are operated / stopped and the compressor operating frequency are changed as appropriate according to the load, and the capacity is controlled. Next, a detailed configuration of the oil separator 3 will be described.
• Fig. 12 is an upper sectional view of the oil separator 3
• Fig. 13 is a side longitudinal sectional view of the oil separator 3.
• reference numeral 50 denotes a shell, which has a cylindrical shape having both ends tapered.
• Reference numeral 51 denotes a cylindrical outflow pipe, which penetrates the vertex portion of the upper taper portion of the shell 50 and is inserted into the inside of the shell 50, between the outflow pipe 51 and the shell 50. It is fixed so that the mandrel is coaxial.
• Reference numeral 52 denotes a discharge pipe, which is fixed to a lower opening 50a formed at the top of the lower taper portion of the shell 50.
• 53 a and 53 b are inflow pipes, each having a cylindrical shape with a diameter of D, and are arranged at the same vertical distance to each other via the central axis of the shell 50, and the inner wall surface of the shell 50, respectively. Are connected in the tangential direction.
• the end 51a of the part of the outlet pipe 51 inserted into the shell 50 is L1 below the center of the shell inner end of the inlet pipe 53a, .53b. Distance, and is located at a distance of L2 upward from the lower opening 50a of the shell 50
• the refrigerant gas from which the refrigerating machine oil has been separated flows out of the outflow pipe 51, and the refrigerating machine oil attached to the inner wall surface of the shell 50 descends on the inner wall surface of the shell by the action of gravity and is discharged from the discharge pipe 52. Is done.
• the pressure loss of the oil separator 3 depends on the diameter of the inlet pipe, one inlet pipe is used to reduce the pressure loss when the refrigerant flow rate for the operation of the two compressors flows. If the diameter is too large, when one compressor is operated, the flow rate will decrease, and the oil separation efficiency will deteriorate due to the decrease in centrifugal action.
• the inflow pipe 53a and the inflow pipe 53b are arranged at the same position in the vertical direction of the shell 50 at equal intervals in the inner circumferential direction, so that the trajectory of the refrigerant gas flowing from one of the inflow pipes is reduced.
• the turbulence of the airflow in the shell 50 can be suppressed, and a decrease in oil separation efficiency when two compressors are operated can be prevented.
• the case where the number of the inflow pipes is two has been described.
• the inflow pipes are placed at the same position (same height) in the vertical direction of the shell, and By arranging them at equal intervals in the circumferential direction, the same effect can be obtained.
• the diameters of the plurality of inflow pipes may be changed according to the flow rate of the refrigerant to be introduced or the capacity of the compressor.
• the distance between the opening of the shell and the inner end of the shell of the outflow pipe is set to be at least five times the inner diameter of the inflow pipe, so that the amount of oil flowing into the oil separator Even if the amount increases, it is possible to prevent a decrease in oil separation efficiency.
• the inner end of the shell of the outflow pipe is located at a position at least five times the inner diameter of the inflow pipe in a downward direction from the center of the inner diameter of the inflow pipe, so that it is wide. The oil separation efficiency can be kept high in the range of the refrigerant circulation amount.
• the inflow pipe has a straight pipe portion connected to the cylindrical portion of the shell, and the length of the straight pipe portion is at least eight times the inner diameter of the inflow pipe. Therefore, the oil separation efficiency when the gas flow rate is small can be improved at low cost. Further, in the oil separator according to the present invention, the inflow pipe has a first straight pipe portion connected to the cylindrical portion and a first straight pipe portion having an angle of 90 degrees in a shell direction with respect to the first straight pipe portion.
• the inflow pipe has a helical shape centered on the central axis of the shell, so even if the installation space is small, This has the effect of improving the separation efficiency. Furthermore, since the shell has a tapered portion formed in an upper part of the cylindrical portion and integrally formed with the cylindrical portion and narrowed upward, compared with a case where the upper portion is formed by a flat lid, The number of points can be reduced, the thickness required to obtain the required strength can be reduced, and the weight can be reduced. In addition, there are a plurality of inflow pipes, and these inflow pipes are connected to the cylindrical portion at the same position in the vertical direction and at equal intervals.
• a compressor the above-described oil separator having an inlet pipe connected to the compressor, a capillary connected to a discharge pipe of the oil separator, and a capillary connected to the discharge pipe.
• a valve connected in parallel, an oil return circuit connected to the capillary and the valve, an accumulator connected to the oil return circuit and the compressor, and a four-way valve connected to the outlet pipe of the oil separator And a heat exchanger connected to the four-way valve, so that the operation efficiency is improved.
• each of the inlet pipes is connected to the above-described oil separator connected to each of the plurality of compressors, and a discharge pipe of the oil separator.
• a capillary a valve connected to the discharge pipe in parallel with the capillary, an oil return circuit connected to the capillary and the valve, an accumulator connected to the oil return circuit and a plurality of compressors, and oil. Since it has a four-way valve connected to the outlet pipe of the separator and a heat exchanger connected to the four-way valve, the operation efficiency is improved. Furthermore, since the valve is opened only when the compressor is started, it is possible to prevent the oil separator from overflowing especially when the compressor is started, in which the amount of oil flowing into the oil separator temporarily increases. .

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• 2000
  • 2000-08-21 JP JP2000249903A patent/JP4356214B2/ja not_active Expired - Lifetime
• 2001
  • 2001-08-07 US US10/088,519 patent/US6574986B2/en not_active Expired - Lifetime
  • 2001-08-07 DE DE60134413T patent/DE60134413D1/de not_active Expired - Lifetime
  • 2001-08-07 KR KR10-2002-7004337A patent/KR100516577B1/ko active IP Right Grant
  • 2001-08-07 WO PCT/JP2001/006771 patent/WO2002016840A1/ja active IP Right Grant
  • 2001-08-07 EP EP01954482A patent/EP1312879B1/en not_active Expired - Lifetime
  • 2001-08-07 CN CNB018024750A patent/CN1232790C/zh not_active Expired - Lifetime
  • 2001-08-07 ES ES01954482T patent/ES2307635T3/es not_active Expired - Lifetime

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